Welding apparatus



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mam TM CLIFFORD S. SELTZER STANLEY M- HUMPHREY any .4 I I D 0 FN co m,.1-

Sept. 18, 1945. c. s. SELTZER ErAL 2,385,109

WELDING APPARATUS Filed Oct. 11, 1941 12 Sheets-Sheet 4 ZjvwcwtomCLIFFORD S. SELTZER STANLEY M. HUMPHREY p 1945- c. s. SELTZER ET ALWELDING APPARATUS Filed Oct. 11, 1941 12 Sheets-Sheet 5 wuowfo c WM/f RE 2 U E 5 Is D R O F W L C STANLEY M. HUMPHREY Sept. 18, 1945. c. s.SELTZER ET AL WELDING APPARATUS Filed Oct. 11, 1941 12 Sheets-Sheet 6I?! a m) 0414M CLIFFORD S.

SELTZER STANLEY M.

HUMPHREY 12 Sheets-Sheet 8 Sept. 18, 1945. c. s. SELTZER ET AL WELDINGAPPARATUS Filed Get. 11, 1941 CLIFFORD S SELTZER STANLEY M. HUMPHREY p13, 1945- c. s. SELTZER ETAL WELDING APPARATUS Filed 001. 11, 1941 12Sheets-Sheet 9 CLIFFORD S. SELTZER STANLEY M- HUMPHREY Sept. 18, 1945.c, s. SELTZER ETAL 2,385,109

WELDING APPARATUS Filed Oct. 11, 1941 12 Sheets-Sheet 1o w I 8 N" II IIIA.

Z l: CLIFFORD S. SELTZER STANLEY M. HUMPHREY Sept. 18, 1945. c. s.SELTZER ETAL 2,335,109

WELDING APPARATUS Filed Oct. 11, 1941 12 Sheets-Sheet ll I v5 0 a M no NY N a a 2 (0 N &

CLIFFQRD S. SELTZER STANLEY M. HUMPHREY Sept. 18, 1945.

c. s. SELTZER ET AL WELDING APPARATUS Filed Oct. ll, 1941 12Sheets-Sheet 12 NN n 9m new 1 mvm wm 9% Q 2 3m AAA//// A E U mvw mom 3m3m 6m 3w HUMPHREY 7W% Patented Sept. 18, 1945 WELDING APPARATUS CliffordS. Seltzer and Stanley M. Humphrey,

Warren, Ohio, assignors to The Taylor-Winfield Corporation, Warren,Ohio, a corporation of Ohio Application October 11, 1941, Serial No.414,624

19 Claims.

This invention relates to welding apparatus and more particularly to anautomatic machine for producing sheet metal cylinders at high productivespeeds. The product may be utilized as bodies of cylindrical metalcontainers or for other purposes and the surfaces of the flat stockmaking up the article may be lithographed,

' coated, or otherwise decorated. The invention, in its broader aspects,combines certain desirable features of the can making and welding artsin a Compact unitary machine for automatically producing sheet metalcylindrical bodies at high productive speeds, which machine, in itsoperation and resulting characteristics, possesses cer-' tainsubstantial advantages as will hereinafter become apparent.

A principal object of the invention is the provision of an automaticmachine for producing sheet metal cylindrical bodies which is'operativeto produce such bodies of gOOd quality from more economical and lessstock than that heretofore employed for the purpose. -Also, theinvention seeks to materially reduce the number of rejectable bodiesformed in machines of this general character and to further materiallyreduce the number of rejectable completed containers whose failurebecomes apparent upon the subsequent application of the container endsor covers.

A more specific object of the invention is the provision of an automaticmachine for securing together the overlapped edges of the formed blanksto complete the fabrication of the cylindrical bodies. The improvementinvolves an electric resistance welding apparatus of specialconstruction which is operative to produce an accurate seam weld ofuniform density throughout the length of the body as results from theapplication of substantially uniform welding current and pressure andsubstantially uniform rectilinear speed of the welding wheel throughoutthe length of the body. This is accomplished without the use ofreciprocating parts in the welding apparatus and involves other noveland meritorious features of construction and operation of the weldingapparatus as will more fully appear hereinafter.

Yet another object of the invention is the provision of an improvedapparatus for welding the contiguous edges of a cylindrically formedsheet of metal which is intermittently moved along its longitudinal axisin the production of cylindrical metal bodies at high speeds. Theapparatus effects the weld with a minimum of excess stock and provides ahomogeneous and uninterrupted weld of improved strength and tightnessthereby contributing to the strength of the finished article andeliminating the possibility of any leaks when the finished article is acontainer. This is accomplished in accordance with the preferredembodiment of the invention by guiding the pre-formed blank over andabout a current carrying horn which forms one operative terminal of thewelding transformer secondaryi'or other source of welding current. Amovable electrode wheel of improved construction and mounting engagesthe outer surface of the overlapped stock edges to effect the weld. Thehorn is provided with inherent means to align the seam edges withrespect to the welding station and to automatically gauge the insidediameter of the cylinder being formed preparatory to the weldingoperation as well as with means to conduct the flow of a liquid coolanttherethrough. Associated with the horn and positioned about its outerperiphery are means to move the formed blank progressively toward thewelding station and off the horn upon completion of the welding cycle,means to frictionally retain the formed blank in its propercircumferential position at the welding station or after the formedblank leaves the contiguous edge guiding device, and means to clamp theformed stock about the horn and against the gauging device at thewelding station after the actuation of the above mentioned frictionmeans and in such manner that the contiguous edges are overlapped inproper manner and without damage thereto.

These and other objects and advantages of the invention will becomeapparent from a consideration of the following detailed specificationand the accompanying drawings wherein there is specifically disclosed apreferred embodiment of the invention.

In the drawings:

Figure 1 is a side view of an assembled ma- 1 chine constructed inaccordance with the principles of the invention;

Figures 2 and 3 are side and end views, respectively, of an electrodewheel sizing bar utilized in the machine of Figure 1;

Figure 4 is an end view of the apparatus of Figure '1;

Figure 5 is a. fragmentary longitudinal section of the mechanical driveassembly of the machine of Figure 1 Figure 6 is a schematicrepresentation of the driving shafts interconnections as the same .ap-

pears from an end of the machine;

Figure 7 is an end view, partly in section, of

the blank stacking and primary feeding mechanism of the machine;

Figure 8 is a side view of a portion of the mechanism of Figure Figure 9is an enlarged view of the lever arrangement employed to maintain aconstant pressure on the lowermost blank in the stack;

Figures 10, 11 and 12 are detailed views of the means employed toadvance the blanks longitudinally through the machine in step by stepprogression;

Figure 13 is a plan view of a portion of the machine, some parts beingshown in section;

Figure 14 is a transverse section throughout the machine, showing thearrangement and drive of the blank notching mechanism;

Figure 15 is a section through a cutter carrying shaft of Figure 11;

Figures 16 and 17 are detailed views of a yieldable abutment and a backstop, respectively, utilized in the machine;

Figure 18 is a transverse section through the apparatus of Figure 1; 7

Figures 19, 20 and 21 are detailed views of the cross feed driving,gauging and clamping assemblies utilized in the apparatus of Figure 1;

Figure 22 is a longitudinal section through one of th forming andwelding horn assemblies;

Figure 23 is a transverse section through the Welding horn atsubstantially intermediate its ends;

Figure 24 is a transverse section of the welding horn at the weldingstation thereof and showing the mechanism employed to clamp the formedblank about the horn;

Figure 25 is an enlarged transverse section of the welding horn at thewelding station;

Figure 26 is a longitudinal section through one of the welding wheelassemblies;

Figure 27 is a view similar to Figure 23 but showing the air and waterconnections more in detail;

Figure 28 is an enlarged sectional view through one of the individualwelding wheel supports;

Figure 29 is a schematic side view of one of the welding wheelassemblies to illustrate the cooling water circuits; and

Figure 30 is a fragmentary side view of the carrier bars utilized totransport the blanks from the forming stations to the welding stationsand beyond.

The apparatus of the invention in its illustrated and preferredembodiment consists of an integrated and self-contained assembly whichis automatically operative to convert flat sheet metal blanks intocylindrical bodies lap welded along their overlapped edges. As such, theapparatus includes a stack for storing a supply of the blanks includingmeans to withdraw the blanks one at a time from the stack, means to movethe individual blanks from the vicinity of the stack to the successiveworking stations of the machine in an intermittent progressive movement,a notching station for removing the four corners of each separate blank,two forming roll stations for forming the flat blanks into cylindricalblanks, a cross feed for gauging, clamping and moving the blanks to theroll stations alternately; a welding station including a currentconducting supporting and gauging horn, as above mentioned, and awelding wheel assembly associated with each of said forming rollstations; and means associated with each of said forming and weldingassemblies to move the formed blank from the forming to the weldingstation progressively. As will appear more clearly hereinafter, all ofthese various parts are supported immediately on a frame In which inturn is supported on a base I i. The latter conveniently houses thedriving and synchronizing apparatus for substantially all of the movingparts of the machine, this apparatus being shown in detail in Figure 5of the drawings. Referring now to this figure, reference numeral I 2designates a shaft which operates all the moving parts of the machinewhich require synchronization and is in turn driven by a motor ll thromh.pulley i4. Shaft 12 is coupled with a countershai't II throughreduction gears I6 and I! which drive shaft I! at half speed. To theouter end of shaft II is keyed a gear II which through meshing gear lldrives a crank 20. A connecting rod 2| for operating the sheetseparating mechanism of the stack, in a manner to be more clearlydescribed below, is connected to the crank 2|. A cam 22 for oscillatinga pivoted arm 22 is provided for the purpose of reciprocating certainsheet feeding bars which will be described below. Also keyed on theshaft II are two angularly spaced cams 24 and 2!, the followers 26 and21 of which are arranged to operate th blanknotching mechanism in amanner to be hereinafter described.

A second countershaft 2| is driven from shaft l2 through reduction gears29 and 30 at onefourth the speed of shaft l2. Keyed to shaft 2| is acollar II having a peripheral groove cam 12, the follower of whichoperates the cross feed mechanism, in the manner to be described below,for the purpose of feeding the blanks to alternate forming rollstations. Collar II is also provided with an axially extending groovecam II, the follower of which oscillates rod 34 for the purpose ofoperating the stock clamp used in the cross feed mechanism. Rod 24 isattached to a yoke II which carries the cam follower engaging the groove33 and has sliding connection with a bearing block 36 which is mountedon the shaft 2|, the whole assembly providing for pivotal movement ofmember 35 about the axis of shaft 22 and at the same time rectilinearmovement of the yoke radially in a manner well understood in the art.

Shaft I2 drives the welding wheel assembly through sprocket 31, chain3|, sprocket II and worm drive 40. Also driven from shaft I! throughgear ll are two spaced parallel countershafts 42 positioned on eitherside of the machine. One such shaft is provided for each of the twoforming and welding assemblies of the apparatus. Each shaft 42 is drivenfrom gear ll by a gear H at one-fourth the speed of main shaft l2.Inasmuch as the two forming and welding assemblies and the componentparts such as, for example, horns, drives and gauging and movingmechanisms are identical, but one such assembly will be described indetail. A cam ll is keyed to shaft 42 and operates rod 40 for thepurpose of operating the expanding gauge block incorporated in thewelding horn to properly size the cylinder body at the welding station.A second cam 41 is keyed to shaft 42 and rocks arm 48 which operates thefeeding bars for transporting the formed blanks from the forming rollstation to and through the welding station. Also keyed on shaft 42 arecams II and II, the functions, of which are to clamp the formed metalblank to and about the welding horn in a manner to be hereinafterdescribed. To facilitate adjustment of the machine, a hand wheel iskeyed onto main shaft l2 whereby the machine may be manually operated.

Blank stacking and primary feeding mechanism Referring now to Figure 7,reference numeral 52 designates stakes which extend vertically onopposite sides of a rectangle to receive and guide a stack 53 of flatsheet blanks. As the first blanks are loaded, they rest at their endsupon balanced levers 54, two of which are positioned at either end ofthe stack. As shown in Figure 9, each of the levers 54 is provided witha downwardly extending projection 55 to limit its downward movement andwith a leg 55 to engage a rounded surface 51 of a check lever 58. Thelower inner edge of each lever 58 is provided with a toe 59 to engagethe end edges of the blanks and prevent the downward movement of thestack of blanks thereabove when the levers 58 are moved to innerpositions. Levers 54 and 58 are mounted on anti-friction bearings andoperate in such manner that the pressure exerted on the end edges of thelowermost blanks in the stack is at all times substantially uniform,being determined by the weight of the blanks intermediate the supportingsurfaces of the levers 54 and the toes 59 since it should be apparentthat as the stack is increased in height, the forces exerted by 58 on 51will move the levers 58 inwardly. The operating characteristic providedby this construction is advantageous since the dead weight resistancelimitations of the feeding mechanism will have no effect on thereliability of the feed and allows the stack to be made considerablyhigher and to vary greatly in height without affecting the operation ofthe machine. This also allows the operator additional time to performother duties required in connection with the operation of the machine.

The invention also provides improved mechanism for removing the blanksfrom the stack individually and this mechanism comprises a suction cup80 carried by the upper end of a reciprocating rod 5| and adapted toengage the bottom surface of the lowermost blank in the stack to drawsaid blank away from the stack. Rod 8| is provided with a centrallyextending bore opening into the vacuum cup 80 and is slidably connectedwith a piston 82 positioned in cylinder 83. The piston 82 isreciprocated by rod 2| from the principal drive of the machine asexplained above and is provided with a flexible washer or cup 84 forgenerating the required vacuum in cylinder 83 above'the piston. Theopening 85 provides communication between this space and the bore of rod5|. The lower end of rod 8| is counterbored and flanged and a coilspring 58 is partially received within the counterbore and engages therear end of bore 51 in piston 82 to resiliently urge the rod 8|outwardly of the piston. An adjustable bushing 88 provides an abutmentfor thefiange of rod 8| thereby limiting the outward movement of therod. Bore 81, however, permits a limited relative movement between thepiston and the rod.

Rotatably carried with the crank 28 is a cam 89 having a follower 18 foroperating the suction relief valve 1 I, which valve is connected withthe vacuum chamber in cylinder 83 by means of conduit 12. A manuallycontrolled valve 1| is connected with conduit 12 and is operative toopen the conduit to the atmosphere when it is desired to manuallyrelease the suction cup 88. Extending longitudinally of the machine oneither side of the vacuum cup is a feeding bar 13 suitably guided forlongitudinal reciprocation and having on its upper surface adjacent itsouter end a fixed finger 14 to engage the side edge of a blank after thesame has been pulled downwardly by the vacuum cup. The construction andoperation of the feeding bars 13 will be described more in detail below.

The operation of the blank separating and primary feeding assembly is asfollows: With a blank resting on the levers 54, the crank 20 .movespiston 82 upwardly and the vacuum cup into pressure engagement with thebottom surface of the blank. The vertical position of levers 54 is suchthat piston 82 continuesits upward movement after movement of rod 8| hasstopped, and until the flange on the latter reaches the lower portion ofthe bore 81. At this time piston 82 commences its downward stroke andthe cup 84 creates a vacuum in cylinder 84 which is transmitted to cup88 through opening and the bore in rod 8|. When the flange on rod 8|engages bushing 88, a substantial'vacuum will have been formed and thecup 80 will be moved downwardly bringing the center portion of thelowermost blank with it. The bottom surface of this blank will nowengage the top surfaces of the feed bars 13 and at this time the barsare moved inwardly to enable the transporting fingers 14 to engage theside edge of the blank. Immediately after fingers 14 engage the blank,the vacuum in cup 50 is broken by operation of cam 89 through valve 1 I.It should be noted that the fingers 14 are provided with overhanginglips to prevent the separated blank from flinging back up toward thestack. A separating cone 18 retains all but the lowestsheet in thestack.

Blank moving mechanism Referring now to Figures 10, 11 and 12, the blankfeeding bars 13 are guided for longitudinal movement in guides 11 and 18and are moved in unison by a block 19 which is connected with outer freeend of lever 23 by means of an adjustable link 80. As explained above,lever 23 is oscillated by cam 22 keyed on shaft I5. Lever 23 is pivotedon a fixed pin 9|. In accordance with usual practice, each of thefeeding bars 13 is provided with a multiplicity of longitudinally spaceddriving fingers so positioned, shaped, and mounted as to produce a flatsquare contact with the side edge of the blank to move the same and todepress beneath it when returning. Heretofore, these fingers were heldin the reciprocating bars by pins about which the fingers oscillatedwithin fixed limits, each finger being provided with a light spring tohold it in its normal operating position. By reason of the limited spacenormally allotted to such mechanism, the supporting pins were not madesufficiently strong to withstand severe conditions of service and,consequently, frequently failed. The present invention avoids thisdifficulty by replacing the pins with abutment blocks 82 (Figure 12),which blocks may be cut to the desired size from a single piece machinedto proper contour as one long length. The bars 13 are each provided witha series of rectangular recesses 83 each of which is adapted to receiveone of the finger assemblies. As shown in Figure 12, the blocks 82 aregenerally square to fit within one end of the recesses 83 and are heldin position by dust plates 84 which plates also limit the outwardmovement of the fingers. A semi-cylindrical recess 85 is provided in theblock '2 and into this recess fits the semi-cylindrical surface of anintegral extension 80 of the finger I1. A leaf spring ll having its endsecured to a block II and bearing intermediate its ends on a shoulder IIis provided to urge the finger 81 to outer position. Block I! and theleaf spring are retained in position by the dust plate 84. The plate Itis provided with an opening through which finger "I extends. The fingersl1 and springs I are likewise cut to the desired width from one longpiece of pre-shaped stock. This procedure results in an assembly ofgreater strength and durability, reduces the costs of the accuratemachining required, and greatly reduces the cost of assembling the bars.The parts are simply dropped into the recesses l3 and retained inposition by the plates 84.

To restrain the blanks in their successive positions to which they aremoved by the fingers II, the ends of the blanks are frictionallyretained by pressure strips 9! which are received within channels 92. Onthe opposite face of the blank ends are continuous members II on whichthe blank ends are supported. To apply resilient pressure between latesSI and I3. semi-flattened soft hoses 94 are inserted within the flangesof channels 92 above plates ll. Side guiding strips 95 are provided toengage the ends of the blank. It should be understood that one guidingand retaining assembly as illustrated in Figure 11 is mounted on eachside of the machine to engage the opposite ends of the blank beinghandled, each assembly being supported on a transversely adJustablemember 98 and the members 96 may be simultaneously moved inwardly andoutwardly by rotation of screw 91 by means of handle 98 in a manner wellunderstood in the art. It should be apparent that the plates 8|, ll andO retain the blanks in the positions to which they have been moved bythe fingers 81 and provide a lateral guide for the blanks. The blankmoving bars 13 extend from the stack station to the cross feed stationof the machine and are operative to progressively move the blanks fromthe stack station to and through the notching station and onto the crossfeed station. Certain types of containers require the removal of thefour corners of the blank preparatory to the fabrication of the cylinderand this is ordinarily accomplished by the use of a punch press of thevertical reciprocating type. The present invention provides an improvedapparatus for accomplishing this operation and the apparatus is suchthat it may readily be incorporated in the cylinder making machine. Thispart of the machine will now be described.

Blank notching station By reason of the method employed in this machinefor making the side seam Joint, a simpler type of notch of cut may bemade at the corners of the blank which greatly simplifies theconstruction and operation of that part of the machine whichaccomplishes this function. In accordance with the invention, thecutting is accomplished by circular cutters revolving about fixed axesand the profile of which is made to correspond to the angle of the cutrequired. Referring now to Figure 13 which is a fragmentary plan view ofa portion of the machine indicating the blank movement preparatory tothe roll forming, such circular cutters are indicated by referencenumeral ill which cutters cooperate with fixed dies iOl. See alsoFigures 14 and 15.

The latter are positioned immediately below the pass plane of the stockand adJustabiy mounted on frame members I02. By referring to Figure 11,it will be observed that the circular cutters I" are notched at I" toreceive the corners of the blanks and the cutting edges are, of course,positioned along the sides of the notches.

The two cutting assemblies on either side of the machine each comprisean oscillating shaft I On which is mounted the two circular cutters I".This shaft is supported in capped bearings I05 supported from bracket 06which in turn is mounted on frame 10 and is oscillated by an arm I"keyed thereto and having pivotal and adjustable connection with aconnection rod I08. Figure 14. The rods III are connected with the camfollowers 28 and 21 (Figure 5) which in turn are actuated by the cams Nand 26 keyed on shaft i5.

Each of the cutters I00 is mounted slidably upon a threaded bushing I"which is provided with the shoulder H0 against which the cutter abutsand on the opposite side of the cutter is positioned a keyed washer Illand a nut III which looks the cutter to the bushing. Bushing I09 isslidably secured to the shaft Ill by lock screws ill and this assemblyprovides an adjustment to accommodate blanks of different lengths aswell as an adjustment to compensate for wear of the cutting edges of thecutter. Likewise, the adJustable mounting of the dies HH provide foradjustment to accommodate blanks of varying sizes and to compensate forwear.

The present invention also includes improved means to align the blankslaterally, longitudinally and angularly with respect to the notchingcutters whereby the notching may be accomplished at a higher rate ofspeed and with greater accuracy. This is accomplished by means of thefollowing devices. Intermediate the stack and notching station are theside guides H4 which tend to maintain the lateral and angular alignmentof the blanks. A similar set of guides is positioned between thenotching and cross feed stations. The blanks advance to the notchingstation by operation of the feeding bars 11 in the manner explainedabove and as the blanks enter the notching station, they are guidedlaterally by fixed side guides I i4 (Figure 13), each of which isprovided with a cam surface at its entering edge. The employment of thelaterally spaced and balanced bars l3 tends also to maintain the angularalignment of the blanks. As the blanks reach the notching station, theyare carried slightly past their final desired location and push backdevices are employed to move the blanks back against positive gaugingstops. These gauging stops, indicated generally by the reference numeralH5 in Figure 13, are shown more in detail in Figure 17. Referring tothis latter figure, a block H i is recessed in plate 98 of frame member96, the block being provided with a dwell H1 in which is received aspring pressed dog Ill normally urged to upper position. Dog III isprovided with an inclined front edge and a vertical rear surface Ill toengage and definitely retain the rear edge of the blank in exactposition. The recesses in plates II are elongated, as indicated inFigure 13, to allow for longitudinal adjustment of the positions ofholders I IS. The dust plates I20 secure the holders H8 in adjustedposition and limit the upward movement of the dogs lit. The means formoving the blanks back against the positive stops I ll compriseassemblies III. one of which is positioned on either side of themachine. Referring to Figures 13 and 16, each assembly consists of amember I22 in which is pivotally mounted a finger I23 mounted forlimited rotational movement about the pin I24. Member I22 is carried byarm I23 keyed to shaft I04. The lower end of finger I23 is provided withan inclined surface I25 to engage the edge of the blank and as memberI22 is moved downwardly, upon rotation of shaft I04 it should beapparent that the surface I25 will force the blank in backwarddirection. An excess movement of the member I22 compresses the springI23 which through thimble I21 urges the finger I23 against stop I20 overmember I22. The positioning assembly, thus provided, accuratelypositions the successive blanks with respect to the cutting edges of thedies MI and cutters I thereby insuring accurately located lines of cut.understood that the leading edges of the blanks engage surfaces I25 ofthe push back fingers I23 before -the shafts I04 are rotated. As shaftsI04 commence their inward rotation, surfaces I25 will move the blanksinto engagement with back stop surfaces IIO before the cutting edges ofthe cutters I00 engage the blanks. The arms I23 are longitudinallyadjustable on the shafts I04 to accommodate blanks of varying lengths.It should be apparent that the positioning and cutting assemblydescribed immediately above possesses many desirable advantages in itssimplicity and economy of construction and operation. The circularcutters I00 as well as the fixed dies IOI may be economically producedand readily maintained in a highly efficient operating condition. Thelatter is true because the design greatly facilitates the grinding ofthe parts to maintain the cutting edges in sharp condition. The anglesof the lines of out are de termined by the conical surface provided onthe cutters I00 and are not disturbed by the subsequent grinding of thecutters.

Cross feed mechanism As explained above, the blanks advanceprogressively from the notching station to the cross feed station and inFigure 13 of the drawings, reference numeral 530 designates the latterstation while reference numeral 53B designates the former station. Theinitial or stack station is indicated at 53A.' The purpose of the crossfeed station is to grasp and move the successive blanks advancingthrough the machine longitudinally in a lateral direction to alternateforming roll stations positioned on either side of the machine and toaccurately guide the blanks into these latter stations. Referring now toFigures 13 and 18 through 21 of the drawings, the cross feed mechanismis slidably mounted on a square rod I30 which is rigidly mounted at itsends in brackets I3I adjustably mounted on fixed frame members I32. Apair of outer flange bushings I33, having openings therethroughcorresponding in contour with the outer surface of I30, are looselyfitted on the slide rod I30 and are provided with outer cylindricalsurfaces to receive needle bearings I34 which are mounted adjacent theflanges. Bearings I34 rotatably mount a semi-cylindrical sleeve I35 forrotation about the center of rod I30 and sleeve I35 is provided with agenerally vertical stop surface I36 and a, horizontal clamping surfaceI31, as indicated in Figure 21.

The main body of the cross slide which is indicated by reference numeralI30 is rigidly secured to bushings I33 intermediate the bearings Itshould be with an upper clampingsurface to cooperate with the clampingsurface I31 of member I35 and with a vertical surface to form anabutment for stop surface I30 of member I35. Member I35 is urged inclockwise direction, as viewed in Figure 21. to normally maintainsurface I36 in contact with the abutment provided on anvil I with theclamp opened, by a coil spring I42 through slidable thimble I43.

Referring to Figure 13, it will be observed that an additional pair ofgauging back stops 5 which are identical with those shown in Figure 1'1are provided at the trailing edge of the position assumed by the blankat the cross feed station. As the blank reaches the cross feed stationits leading edge abuts the surface I36 thereupon rotating member I35 ina counter-clockwise direction (as viewed in Figure 21) and the edge isthus clamped between surface I31 of member I35 and anvil I. In movingthe blank into engagement with surface I36 the stock advancing fingers31 move the trailing edge of the blank past the gauging surfaces I I3,of stops I I5 causing the blank to arch slightly and upon retraction ofthe fingers 31 the trailing edge of the blanks moves into firmengagement with the surfaces II3. At this time the blank is properlyaligned and firmly clamped along a substantial extent of its principaldimension.

. To move the slide to alternate roll forming stations the followingmechanism is provided:' Extending downwardly from the slide body I38 isa boss I44 to which is pivotally connected a lever I45, Figures 19 and20. Lever I45 is in turn pivotally connected with a block I46 which isslidably mounted in a window I41 of lever I40, a screw I49 beingprovided to determine the position of the block in the window. Lever I40is keyed to a vertically extending shaft I50 which is journaled in aframe support I5I. To the lower end of shaft I50 iskeyed a lever I52which carries a cam follower I53 ,at its outer free end to engage thegroove 32 of cam 3| to oscillate the parts upon rotation of shaft 26 inthe manner explained above. It should be apparent that as the cam 3Irotates, the cross feed slide I33 and its auxiliary parts will be movedalong rod I30 from one side of the machine to the other and the extentof such movement will be determined by the adjustment of screw I40.

To provide for unclamping the blank from the cross feed, after one ofthe two sets of forming rolls has firmly engaged the blank, the anvilI4I is pivoted for movement toward and away from the surface I31, asexplained above, and an eccentric pin I53 journaled in a bearing I54 isprovided to move the anvil toward and away from surface I31. A sleeveI55 surrounds pin I53 and engages a plane surface on the under side ofthe anvil to normally maintain the anvil in raised position even duringtransverse movement. Pin I53 is adapted to be rotated by an arm I56which is keyed thereto and in turn pivotally connected with the upperend of rod 34. See Figure 18 The operation of the assembled apparatus issuch that as the slide I38 approaches the end of its outward or feedingstroke, the cam 33 through rod 34 and arm I 56 rotates pin I53 allowinganvil Hi to drop. This occurs shortly after the blank has been firmlyengaged by the forming rolls. At this time the clamp is released but asit returns to its center position in preparation for the reception ofthe next succeeding blank pin I53 is rotated back to its normal positionto again raise the anvil. An important advantage of the improvements inconstruction of the cross feeding station disclosed herein is that theblanks are accurately positioned and aligned before entering the rollsof the forming stations thereby insuring the proper operation of thelatter and an accurately formed blank. Another advantage is that theedge of the blank is securely clamped throughout a substantial portionof its extent as it is fed into the forming roll pass thereby reducingsubstantially the probability of buckling of the blanks.

Forming stations Each of the roll forming stations comprises essentiallya pair of driven pinch rolls, a deflecting or bending guide, and acylindrical guide into which the stock is propelled by the rolls. Thepresent invention, however, provides improvements in the arrangement andconstruction of the various parts involved whereby the deficiencyheretofore inherent in similar devices, which is to the effect that theformed blank includes a small unrolled area at the lagging edge of theblank, is obviated. This small flat area occurs where the lagging orfinal edge of the metal passes through the driving rolls and continuesto the deflector guide. Another deficiency sought to be corrected by thepresent invention is the elimination of any possibility of slippagebetween the rolls and the stock, which slippage may result in skewing ofthe blank and stoppage of the machine. Slippage occurs due to unevennessin the thickness of the stock and is not satisfactorily avoided byhaving one rolled spring mounted and both rolls accurately sized forconcentricity and parallelism.

Referring now to Figures 13, 18 and 20 of the drawings, referencenumeral I50 designates a cylindrical form about which the rolled blank,

is encompassed. Joumaled in the form member I58 is the lower formingroll I50 whose axis is so chosen that the outer surface of the roll istangent to the periphery of the outside surface of the member I50. Asecond forming roll I60 is journaled in suitable bearing blocks II flxedto the machine frame outside of the member I58. Rolls I50 and I00 aredriven by a motor I 62 mounted on the bracket I03 positioned above theforming station, the motor being connected through drive I04 keyed ontothe end of the roll shafts. Immediately in back of the rolls I 50 andI60 is a, deflecting plate I51 which is adjustably mounted at I50 and isprovided with a knife edge to receive the stock as the same issuesthrough the roll pass to thereby bend the stock downwardly. A guide I09is positioned above the path of travel of the stock immediately in frontof the pinch roll pass.

ASrShOWl'l in Figure 18, the cylindrical form I58 is flattened along thechord I10 to provide for the mounting of roll I59 and supported on thechord to one side of the roll is a block I1I having an outer surfacecoincident with the periphery of form I50 and a tongue I12 which isadapted to be received in an annular recess I13 (Figure 22) of the rollI50. This construction eliminates the possibility of the blank rollingtoo sharply and becoming encompassed about the bending roll I50.Positioned on the chordal Plane I10 on the opposite side of roll I50 isa second block I10 provided with a stop I15 to engage the advancing edgeof the blank as it passes about the form I50.

The axes of rolls I50 and I50 lie in a common vertical plane which isspaced outwardly of the vertical plane including the principal axis ofthe cylindrical form I50. This construction, it is found, eliminates thesmall unrolled or uncurved area adjacent the lagging edge of the blanksince the deflecting surface of member I61 is coincident with thecylindrical curve of the form I50 and has its leading edge closelyadjacent the pass between the rolls I50 and I00. This arrangement is notpractical without the offset since then the leading edge of member I51would possess insuflicient strength to deflect or bend the blanks. Whenthe rolls I50 and I60 receive the near edge of the advancing blank, theblank is driven at greatly increased speed under the bevelled edge ofthe blade I51 and about the form I50. The momentum imparted to the blankmoves the advancing edge thereof into engagement with stop I15 in whichposition of the blank, the lagging edge thereof is entirely free of therolls.

Pivoted at I15 for rotation about an axis parallel with the principalaxis of cylinder I50 are the guide wings I11 and I10, one positioned oneither side of the form I50, provided with curved surfaces to overliethe periphery of form I50 thereby insuring that the blanks will havesliding contact with the form. The guide wings are held inwardly byspring pressed thimbles I19 which engage the wings intermediate theirtops and bottoms. The wings with their resilient mounting serve as aprecaution against blanks being passed through the forming stations withan improper curve and allow for expansion of the restraining surfaces inthe event that the blank becames buckled. Each of the wings I11 and I10is provided with two circumferentially spaced but axially extendingrecesses I00 adapted to slidably receive the carrier bars IOI. Asindicated in Figure 18, the recesses I00 extend radially outward fromthe inner curved blank guiding surfaces of the wings I11 and I10 andwhen the parts are assembled, the inner surfaces of the carrier bars IOIcoincide substantially with the curve of the blank. Bars IOI each haveretractable blank moving fingers I02 (Figure 23) and shallow slots I00in the outer surface of cylindrical form I50 are provided to accommodatethe outer edges of the fingers. The carrier bars IOI are provided totransport the rolled blanks from the forming stations to the weldingstations in a manner to be hereinafter described. I

One of the driving rolls, preferably I00, is preferably constructed byemploying a soft oil-proof cylindrical cushion I00 about the shaft I05(Figure 22) and covering the cushion with a metal casing I00. Thisconstruction permits the roll to firmly contact the surfaces of theblanks regardless of variations in their thickness and thereby preventsslippa e between the rolls and the blanks. Consequently, the blanks aredriven into the cylindrical confining space between form I50 and theguiding wings I" and I10 in even and properly aligned relation.

Welding stations-Current conductive transporting horns Longitudinallyaligned with each of the cylindrical forms I50 is a current conductingblank transporting and welding horn I88 which is carried by the fixedframe of the machine and in rigid alignment therewith by thetransversely extending carrier bar I88 which is insulated with respectto the frame of the machine. Figures 22, 23 and 24. A finger bar andbody guide I98 loosely embraces the horn I88 and is supported from theframe I8. As indicated in Figure 23, guide I98 is provided withlongitudinally extending recesses to receive the carrier bars I8I andthe looseness of the guide permits the pre-formed blanks to travel overthe horn and within the guide longitudinally. Bars I8I are secured to asleeve I92 which is oscillated by an adjustable lever I93 from arm 48.It should be understood that the circumferentially spaced bars I8Iextend from about the form I88 to about the horn I88 to the vicinity ofthe welding station and thus provide a carriage for moving thepre-formed blanks to the welding station upon oscillation of arm 48.Cylindrical form I58 is larger in diameter than the diameter of thecompleted cylindrical body being produced so that as the blank leavesthe form and passesonto the conducting horn I88, the cleft edges of theblank are spaced apart, and integral with the horn I88 is an upwardlyextending longitudinal web I94 which aligns the formed blank angularlyon the horn during movement of the blank by engaging the cleft edges ofthe blank. Incidentally, the web I94 provides a means of supporting thehorn. Extending upwardly from one end of the web I94 is a terminal I85to which one terminal of the welding transformer or other weldingcurrent supply is adapted to be connected. Extending laterally outwardfrom either side of terminal I95 is a wing I98 on the lower surface ofwhich is adapted to be secured a wiping device, not shown, to cooperatewith a wiping device supported on the horn itself to clean both theinner and outer surfaces of the stock adjacent both cleft edges.

The outer or welding end of horn I88 is provided with a laterallyslidable gauging segment I91 (Figure 24) which is operative to expandthe blank outwardly to accurately size the inner diameter of the blankat the welding station. A pair of spaced squared cam followers I98,received in aligned recesses in the body and segmental portion I91 ofhorn I88 and bearing against the inner ends of screws I99 (Figures 24and 25) screw-threadedly received in the segment I91, are adapted tomove the segment I91 laterally outward. Followers I98 are arranged to beoperated by machined cam surfaces on rod 288 which is slidably receivedin a longitudinal bore provided in horn I88. Referring to Figure 22, rod288 is operated by a pivoted arm 28I through connecting rod 48 from cam45. The operation of this mechanism is such that after a particularblank has assumed its, proper position at the welding station, cam 45acts to expand the horn at the welding station by moving gaiging segmentI91 outwardly to insure the proper diameter of the completed cylindricalobject. Segment I91 is substantially co-extensive in length with thebody being produced. As the formed blank passes from the cylindricalform I58 onto the horn I88, the inwardly directed edges of the blankpass on opposite sides of the lever 28I which is flattened. In additionto the features specifically described, the horn is constructed withpassages to permit cooling water to freely flow to and away from itsextremity at the welding station and the inlet and outlet for suchpassages also extend through the web I94. A welding spline 282 isassembled to the horn at the welding zone and a wearing segment 288 issecured to the horn at a point diametrically opposite the spline 282.

Welding station-Stock clamp Associated with the horn m at the weldingstation is a compound clamping assembly which is operative to firstclamp the blank to the horn at a point diametrically opposite thewelding zone to prevent angular misalignmentof the blank relative to thehorn and welding zone, to overlap the edges of the blank, and thereafterto securely clamp the stock against the expanded sizing horn preparatoryto the actual welding operation. For this purpose a clamp bar 284(Figure 22) is positioned opposite the segment 288, being adapted toengage the outer surface of the blank and on either side of the bar 284is a clamping wing 285 which is accurately machined on its inner surfaceto accurately embrace the expanded welding horn with the blank bodytherebetween. Wings 285 are pivoted on a pin 288 which extends exactlyparallel with and below the line of weld, the pin being journaled in asupport 281 extending upwardly from the base I8. One of the wings iskeyed to pin 288 to rotate the same and also keyed to pin 288 is aneccentric 288 which forces bar 284 upwardly upon rotation of pin 288 asrepresented by an initial movement in a closing direction of the saidone of the clamping wings. Each clamping wing is operated by a toggle289 operated by a cam follower 2I8 bearing against one or the other ofthe earns 49, 58. The two cams 49 and 58 are identical but are angularlyspaced so that one of the wings 285 will close before the other of thewings. This arrangement insures that one of the blank edges will bedeposited on the welding spline 282 (Figure 24) before the other of theedges is brought into position thereby insuring the proper overlappingof the edges preparatory to the welding operation. Obviously, the firstwing to move during the clamping operation rotates the pin 285 and theconstruction of cam 288 is such that the blank is rigidly clampedbetween 283 and 284 before the first wing progresses any appreciabledistance along its path of movement. Upon completion of the weldingoperation, the clamps 284 and 285 move away and the carrier bars I8Iforce the completed cylindrical body off the end of the welding horn andalong the conveyors 2.

Welding stations-equipment An important part of the present invention isthe improved features of construction of a semicontinuous seam weldingmechanism which is capable of such regulation and control in all of itscritical phases that the welding of thingauged stock normally employedin making cans may be satisfactorily accomplished at high rate of speed.Heretofore, seam welding has been accomplished either by passing thework progressively between the welding electrodes or moving theelectrodes in relation to the work and either of these methods requiresa reciprocating action of comparatively heavy mechanism. At hi h speedsthe forces thus developed introduce definitetendencies toward inaccurateresults and a very brief life of the mechanism involved. The presentinvention overcomes this disadvantage by eliminating the need for anyreciprocating parts in the electric welder assembly. This isaccomplished byemployin a plurality of circumferentially spaced weldingwheels which are mounted for orbital movement about an axis parallelwith the axes of rotation of the individual wheels. The entire assemblywhich is of substantial mass is arranged to be continuously rotated inthe same direction and properly correlated in position and speed withthe means employed to convey the pre-formed blanks to the weldingstation so that one of the wheels will traverse the overlapped edges ofthe blank immediately upon the blank being positioned at; the weldingstation, while the intervals between the succeeding wheels provide off"times during which the completed product may be removed from the weldingstation and a new blank brought into position. The invention alsoinvolves various other novel features of construction which will becomeapparent from the following description of a preferred embodiment of thewelding apparatus.

Referring to Figures 22, 26, 27 and 28 reference numeral 2l3 indicates adriving block which is keyed to a shaft 2 journaled in a conductivebearing 2i5. Bearing 2|3 encompasses a current carrying bushing 2i3which extends outwardly of the bearing 213 and into the hub of thecurrent carrying disk 2". The other terminal of the welding transformersecondary or other source of welding current is adapted to be connectedwith the bearing 2".

A disk 2I3 extends radially outward from one end of block 213 and asecond disk 2| 3 extends radially of the other end of the block 2I3. SeeFigure 26. Intermediate the two last mentioned disks are a plurality ofradially extending but circumferentially spaced hollow studs 223, eachof which carries a piston 22i at its outer end, and the openings throughthe studs 223 cooperate with a central bore 222 in shaft 2 to providepassages for air under pressure to the outer sides of pistons 22i.

Positioned intermediate the disks 2" and 2l9 are a plurality of weldingwheel supporting blocks 223 which are guided longitudinally by the disksand circumferentially by the guiding surfaces 223 and 223 provided bynotching the disks 2" and H3. Each of the blocks 223 is provided with abore into which is forced a sleeve 223 to constitute a cylinder for oneof the pistons 22!. Any number of welding wheel assemblies may beemployed, depending on the size and desired capacity of the machine butin the embodiment specifically disclosed, eig'ht such wheels areemployed. Blocks 223 are provided with capped bearings 221 and 223 toJournal shafts 223 which carry the welding wheels 233. Extensions 23iare secured to blocks\223 and flexible conductors 232 connect the disk2!! with the blocks 223 to provide for the conduction of welding currentto the individual welding wheels.

In the embodiment of the invention specifically disclosed, there are twowelding wheel assemblies 2| 3-232, one on either side of the machine tocooperate with each of the two forming stations and these assemblies areboth driven from a common drive positioned therebetween. This driveconsists of two shafts 233, one for each assembly, suitably journaled,and to these shafts 233 is keyed a single worm wheel 233 meshing withthe worm 33 which, as explained above, is driven by chain 33 from mainshaft i2. Figure 5. The outer ends of shafts 233 have flanges 233 to theouter periphery of which are attached rings 233 of insulating material.Rings 236 are in turn frictionally retained with respect to the disks M3by the clamping rings 231, which are secured to the disks 2i 3. Thus, aninsulated drive is provided for each of the two welding wheelassemblies.

When air is supplied to the passage 22, each of the carrier blocks 223is urged outwardly by the air pressure existent in the cylinders 223radially outward of the pistons 22L Outward movement of the carrierblocks, however, is limited by a continuous track 233 (Figures 1 and 26)against which a roller 233 carried by each of the blocks 223 is adaptedto abut. The track is of such contour, however, that as the weldingwheels 233 reach the welding spline 232 outwardly of the end of the seamto be welded, the rolls 233 are lifted from the track by reason of theengagement of the wheels 233 with 232 and upon the traverse of the scam,the full pressure of the air within the cylinder 223 is operative forapplying the welding pressure. Thus the welding pressure may be readilyvaried by controlling the air pressure in bore 222. It is found that thewelding pressure applied is substantially constant throughout the entiretraverse of the seam since the substantial interval between the axis ofsupporting shaft 2 and the working surface of spline 232 results in butlimited and relatively slow inward movement of the blocks 223 therebyallowing the slight increase in air pressure to be dissipated throughoutthe substantial spaces of the air system. It should be also observedthat the supporting axis of shaft 2 is positioned centrally above thespline 232 (Figure 22) and this together with the relatively shortlength of the spline as compared with the interval between the workingface of the spline and the said axis results in but a smallinconsequential variation in the welding speed as the welding wheeltraverses the spline.

To provide for cleaning and sizing the wheel electrodes 233 during theirorbital movement and between their successive uses at the weldingstation, a sizing bar 2'" (Figures 1, 2 and 3) is provided for each ofthe rotary assemblies, being mounted on the machine in position to beengaged by the electrodes. Bar 2' is constructed with a longitudinallyextending groove 212 having a transverse outline identical with thatdesired on the periphery of the electrodes. The electrodes move into thegrooves during their orbital movement and when contact is made therollers 233 leave track 233 allowing the pressure exerted by cylinders223 to hold the electrodes in pressure engagement with the sizing bars.In practice, the bars 2'" are made sumciently long to insure suchengagement for the entire circumferential extent of each electrode. Inthis manner the proper transverse contour of the welding wheelperipheries is maintained.

Referring now to Figures 27, 2B and 29 which show the air and waterconnections for the electrode wheel assembly, a distributor 2 is screwedinto the bore 222 of shaft 2I3, the distributor being provided with aflange 232 to over-lie the end of the shaft 2. Assembled outwardly ofthe bearing 2" is a housing 233 having a capped end 233 and a bore toreceive a cylindrical portion of the distributor 2. The latter isprovided with a center bore 233 which is opened to the space in 233, thelatter being connected with an air supply conduit 233. Member 2 isprovided with two other longitudinally extending passages 231 and 233which communicate with annular distributor recesses 233 and 233,respectively, formed in the bore of 233. The first recess is incommunication with a water supply

